Cylinder printing machine



May 19, 1959 CYLINDER PRINTING MACHINE Fil ed Nov. 1, 1955 4Sheets-Sheet 1 H. I g mm" Gn-aIIIIIIIIIIU-P-III---I---=j== I May 19,1959 HANS-BERNHARD S CHUNEMANN CYLINDER PRINTING MACHINE 4 Sheets-SheetZFiled Nov. 1, 1955 HANS-BERN HARD SCHUNEMANN I May 19,1959

CYLINDER PRINTING MACHINE 4 Sheets-Sheet 3 Filed Nov. 1, 1955 May 19,1959 HANS-BERNHARD SCHUNEMANN 2,385,973

CYLINDER PRINTING MACHINE Filed Nov. 1, 1955 4 Sheets-Sheet 4 UnitedStates Patent i CYLINDER PRINTING MACHINE Hans-Bernhard Schiinemann,Wurzburg, Germany, assignor to Schnellpressenfabrik Koenig 8: BauerAktiengesellschaft, Wurzburg, Germany, a corporation of GermanyApplication November 1, 1955, Serial No. 544,268 1 Claims priority,application Germany June 10, 1955 11 Claims. (Cl. 74-27) The inventionrelates to a cylinder printing machine with a uniformly rotatingimpression cylinder and a carriage whose return movement is faster thanits forward,

stroke and the stationary fixed driving-wheel of which engagescontinuously with a spur-rack on the carriage.

Attempts have already been made to drive the carriagedriving shaft withtwo counter running toothed segments in alternating directions, andbraking and accelerating was to be done by a spur-rack that was to becontrolled in a form-locked fashion by curved-disks. Experience hasshown that obtaining shock-free engagement with a uniformly rotatingtoothed drive by means of curve-disks is very difficult, especially whengreat forces have to be controlled as they do occur in the case ofbraking the carof a cylinder printing machine with uniformly rotatingimpr ession cylinder and a carriage whose return movement is faster thanits forward stroke is effected by means of two differing and alwaysalternatingly acting gears that are similar to Maltese crosses. Suitablefor the purpose,

according to location, are true Maltese crosses, open Mal-Q tese crossflank pairs with enclosed toothed segment, and similar gears. Crosseswith differing divisions are especiallyused in order to provide the maindriving shaft with ample time for accelerating and retarding at thehigher return speed. Obtaining approximately equally high acceleratingvalues for forward running and return move ment is thus made possible inan advantageous way. Furthermore, the entire carriage path is keptshort.

Figures 1, 2 and 3 show by way of example three different versions ofthe invention for two-revolution presses. Figure 4shows a pressaccording to Figure 3 in cross section. The invention, however, allowsalsofor combinations of these arrangements and further versions.

. With an arrangement according to Figure 1, a shaft 18 with gearsthereon drives uniformly rotating single-revolution wheels respectivelyon shafts 2 and 11. Single. revolution shaft 2 is connected withimpression cylinder by an intermediate wheel which can be seen to theright and above the carriage driving wheel 1. This single-, revolutionshaft 2 provides for the movement of the carriage through the printingmotion pushers and rollers 3 and 4 at each arcuate end and within thepitch circle of toothed segment 5 attached to the single revolutionwheel on shaft 2. These pushers cooperate as pushing and braking rollswith open Maltese cross straight flanks 6 and wheel 34 of carriagedriving shaft 27 and acts as a re- Patented May 19, 1959 flank anddriving flank 6 attached to the carriage driving shaft 7 sets thecarriage moving and after a turning of 45 degrees brings the toothedsegment 5 into bump-free driving engagement with the driving wheel 8afl'lxed to shaft 7. As this occurs the forward motion of the carriage Sis in synchronized running with the impression cylinder 20. At the endof segment 5 the other pusher 4 contacts the braking flank portion 9 ofthe open Maltese cross flank and brakes the carriage driving shaft 7down to speed 0, so that the pusher 4 subsequently leaves its brakingflank 9 in a tangential fashion. At this moment, a second uniformlydriven single-revolution shaft 11 takes over the return movement of thecarriage at the same swinging angle of the carriage driving shaft 7 asthat of the forward running movement. Toothed segment 14 of thesingle-revolution shaft 11 also has a pusher roll and a braking roll 17at the ends thereof. The turn-table mounting the respective straightflanks 12 and 16 is affixed on shaft 19 of a reduction gear segment orspeed change drive 13. The pusher roll 10 runs into its pushing flank 12and starts the reverse turning of the carriage driving shaft 7. Pusher10 with shaft 11 travels an even 60 degrees before its toothed segment14 meshes with the toothed segment 15 of the counter shaft 19 andreduction gear segment 13 meshes with wheel 8 of the carriage drivingshaft 7 so as to uniformly move the carriage.

Subsequently, the other flank 16 brakes with its roll 17 the quickreturn motion. Braking roll 17 leaves its flank 16 in a tangentialfashion at the moment of dead center position of the carriage at thesame time, pusher 4, as shown at the right in Figure l enterstangentially against its pusher flank 6. Both main driving shafts 2 and11 rotate together with pushers in the same direction and' which worktogether with the straight flanks 28 and 29 respectively of a Maltesecross gear turn-table which is wedged onto the carriage driving shaft27. The toothed segment 22 carries furthermore at a corresponding radiusdistance a further pusher 25. Pusher 25 causes the accelerated returnmotion of the carriage. Pusher 25 cooperates with a balancer 26 oftoothed segment 32 on auxiliary shaft 33 which meshes continuously withthe driving ancer 26 and pusher 23 causes the forward movement of thecarriage via the pushing flank 28 of carriage driving shaft 27.. Afterthis, toothed segment 22 in mesh with 1 driving wheel 34 of shaft 27takes over the uniform printing action until braking roll 24 with itsbraking flank 29 of carriage driving shaft 27 effects the retardinguntil standstill of the carriage before reversal. The toothed segment ofthe balancer 26 always remains in mesh with the driving wheel 34 ofshaft 27 and is, therefore, upon =tangentially leaves its braking flank29. For driving the I At the moment of reversal carriage the toothedwheel 30 wedged on shaft 27 cooperates with spur-rack 31 of thecarriage.

In a further version of the invention, Figure 3 shows two uniformlyrotating single-revolution main driving shafts 43, 44 which arecountercurrently driven in a more or less known fashion by means oftheir meshing, toothed wheels 41, 42. Each shaft carries one of thetoothed segments 45, 46 differing in length and diameter, whichcooperate with the toothed segments 47, 48 of carriage driving shaft 49and which within the pitch circle are at both ends flanked by a pusherand braking pair of rolls 50, 52 or 51, 53 respectively. Here, too, thepusher roll 50 and braking roll 52 cooperate respectively with pusherflank 54 and braking flank 56 to cause smooth acceleration andretardation of the carriage to speed 0. So also the pusher roll 51 andbraking roll 53 cooperate respectively with the pusher flank 55 andbraking flank57 at each end of segment 47. Both turn-tables of allbraking and pushing flanks are stationary wedged on carriage drivingshaft 49. in contrast to Figure 1, the differing Maltese crosses are notadjusted to the same turning angle of the carriage driving shaft atforward and return motion by means of a reduction-gear, but by means ofthe curved shape of pushing and braking flanks 55, 57' which actas speedchange drive coupling. Thus, it can be obtainedv that the main drivingshaft allows for more time, i.e., greater rotation angles, foraccelerating and retarding the high return speed than for the smallerforward motion speed. Here again it is possible to make acceleratingmovements at forward and return motion practically equal, which resultsin the smallest possible accelerating in the entire machine. The curvesof the flanks 55 and 57 may be shaped more or less at will, however,exact circular cylinder pieces are especially advantageous from amanufacturing point ofview. Should in the known fashion cycloidallyshaped forms be chosen, the flank curves may then be shaped as lockedguiding-slots by means of which auxiliary curves are no longer required.With carriage driving shaft 49 there is a toothed segment connectedwithin the machine, which continuously meshes with spurrack 59 ofcarriage 60. Impression cylinder 61 is driven by single-revolution shaft43 via an intermediate wheel 62. Intermediate wheel 62 is therebysituated almost horizontally to the cylinder, so that lifting thecylinder practically does not cause any increase in teeth back-lash.Driving the cylinder can also be effected by driving shaft 44 viatoothed wheel 42. In addition to the open pushing and braking'flanks,all gears shown possess guidings which at slow running of the machinehold the pushing and braking rolls at the flanks, i.e., guide these in aform-locked manner. These guidings act as auxiliary curves which do notabsorb the dynamic forces and are correspondingly less heavy inconstruction. For the sake of illustrating them well, they have onlybeen indicated in Figure 2 under 34 and 35, without being limited tothisarrangement.

It may be mentioned that these Maltese cross-type gears may be shapedfor external switching, internal switching or as. straight guidingswithspur-racks. In the latter case there are by way of example four-thirdrevolution shafts switching with alternatingly acting pushers.

The gears according to the invention can be housed in a more or lessclosed-up gear-box in the known manner. Figure 4 shows a cross-sectionthrough a press, according to Figure 3. side frame II, there is runningin an oil bath the reversing gear, from which the carriage driving shaft49 leads into the machine, carryingthe carriage driving wheel 58. Thismeshes continuously with spur-rack 5 of the carriagefitl which is led inthe conventional manner. The deep'level of shaft 49 has in the low levelof the carriage a favorable effect. By means of a reduction gear, it ispossible to increase the rotating angle of shaft 49 andto locate thecarriage on a deeper level.

example, would receive its drive from the single-revolu- Outward to theleft, in front of machine.

Impression cylinder 61, for

4 tion main driving shaft via an intermediate wheel 62 within gear-box63.

Main driving shafts of the multi-revolution type may be envisaged forall cases, however, these gears are unable to work on the same level.Couplings would then have to be provided or lateral shifting of thedriving wheels would become necessary. Against this, the examples givenof gears with single-revolution main driving shafts distinguishthemselves by their simple design, their small. highest accelerationsand their small depth in construction.

What I claim is:

1. In mechanism for transmitting alternating forward and rearwardrotation to a reverse motion shaft, gear means fixedly mounted on saidshaft, a first Maltesecross type drive means meshing with said gearmeans and having a driving angle for rotating said shaft in onedirection representing advance travel, a second Maltesecross type drivemeans meshing with said gear means and having a driving angle of alarger size as compared with the driving angle of said firstMaltese-cross type drive means for rotating said shaft in a reversedirection representing return travel faster than in the advance travel,said first and second Maltese-cross type drive means having pusher andbraking flanks, pusher and braking rolls corresponding to the flanks andassociated toothed segments for meshing engagement with said gear means,and synchronizing and speed change drive means interposed between saidgear means on the reverse motion shaft and one of said Maltese-crosstype drive means for synchronizing corresponding rotating angles at theend of one direction of rotation of the reverse motion shaft and thegear thereon and the beginning of the reverse direction of rotation ofsaid reverse motion shaft' and the gear thereon and between suchsynchronizing accelerating, changing the speed of drive and deceleratingthe drive of said reverse motion shaft.

2. In mechanism for transmitting alternating forward and rearwardrotation to a reverse motion shaft, gear means fixedly mounted on saidshaft, 2. first constantly rotating shaft spaced from said reversemotion shaft, a first gear segment mounted on the first shaft, a pusherand a braking roll mounted respectively at the ends of said segment, anintermediate shaft mounted intermedi-- ate said reverse motion shaft andsaid first shaft, a first Maltese-cross like gear means having asegment, a pusher flank means and a braking flank means mounted on said"intermediate shaft for driving and braking engagement by said segmentand rolls on the first shaft, a reduction gear segment fixed to theintermediate shaft and meshing with said gear means on the reversemotion shaft, a. second constantly rotating shaft rotating at the samespeed as the first shaft and in the same direction, a secondMaltese-cross type drive means including a gear seg:' ment on the secondshaft for meshing with said gear means on the reverse motion shaft, apusher roll and'a braking roll at each end of said last named gear SE8?-ment and a pusher flank and a braking flank fixed tosaid reverse motionshaft and for cooperative driving action with said respectively lastnamed pusher and braking rolls for driving the reverse motion shaft in areverse direction of rotation and at a higher angular speed of rotationthan said first shaft, said reduction gear segment and said meansmounted on the intermediate shaft acting as speed change drive means andsynchronizing,

means for synchronizing the speed of rotation of said,

reverse motion shaft at the end of one direction of rotation with thespeed of rotation at the beginning of the reverse rotation of thereverse motion shaft and changing the speed of dri e of the reversemotion shaft.

3. A mechanism according to claim 1 wherein said intermediate shaft ispositioned intermediate said second.

shaft and said reverse motion shaft, said first Maltesecross type gearmeans on the intermediate shaft having;

engagement with the gear segment, pusher braking rolls assaors on thesecond shaft respectively and said gear segment, pusher and brakingrolls on the first shaft having cooperative engagement with said flanksand gear means of the reverse motion shaft.

4. In mechanism for transmitting alternating forward and" rearwardrotation to a reverse motion shaft, gear means fixedly mounted on saidshaft, a constantly rotating shaft, a first Maltese-cross type drivemeans for drivsaid gear means and reverse motion shaft in one direction,including pusher and braking flanks fixed to said reverse motion shaft,a gear segment fixed to said constantly rotating shaft for meshing anddriving engagement with said gear means on the reverse motion shaft, apusher roll and a braking roll at the ends of said gear Segment and fordriving and braking action with said flanks, an auxiliary shaft, anarcuate gear segment pivoted on said auxiliary shaft and meshing withsaid gear means to drive said reverse motion shaft at a different rateof rotation than said first Maltese-cross type drive means and in partof its arcuate travel causing a rotation in a synchronizing manner ofthe reverse motion shaft at one end of its arcuate travel in onedirection with the beginning of its arcuate travel in the reversedirection, said arcuate gear segment mounted on the auxiliary shafthaving a balancer drive affixed thereto of a true Maltese-cross, saidconstantly rotating shaft having a pusher arm means fixed thereto with apusher thereon forldriving engagement with said balancer drive therebydriving said arcuate gear segment in one direction when not being drivenin the reverse direction by said first Maltese-cross type drive means.

5. In mechanism for transmitting alternating forward and rearwardrotation to a reverse motion shaft, said reverse motion shaft having ahigh speed gear segment and -a low speed gear segment thereon, a firstconstantly rotating shaft, a second constantly rotating shaft rotat ingat the same speed but in a reverse direction from said first constantlyrotating shaft, a Maltese-cross type drive means drivingly disposedbetween the first constantly rotating shaft and the low speed gearsegment and including a gear segment, a pusher and a braking flank andpusher and braking rolls for respective cooperation with said flanks, aMaltese-cross type drive means drivingly disposed between the secondconstantly rotating shaft and the high speed gear segment on the reversemotion shaft and including a gear segment, pushor and braking flanks andpusher and braking rolls respectively for cooperation with the lastnamed flanks, said last named flanks being shaped for cooperation withtheir respective pusher and braking rolls to drive the reverse motionshaft at a rotation rate at the beginning of its high speed reversemotion that is equal to the rotation rate at the end of its just priordirection of rotation thereby synchronizing the deacceleration speed ofprior direction of rotation with the acceleration speed at the beginningof said reverse rotation.

6. In a mechanism according to claim 5 wherein the flanks of the firstMaltese-cross type drive means are straight flanks and the flanks of thesecond Maltese-cross type drive means are exact circular arcs.

7. In combination in a cylinder printing press with uniformly rotatingimpression cylinder, a carriage having a spur-rack thereon, a drivingwheel continuously meshing with the spur-rack, a forward and rearwardrotation shaft having fixedly mounted thereon said driving wheel, areversely driven gear fixed on said shaft, a first Maltesecross typedrive means meshing with said reversely driven gear having a drivingangle size for moving the carriage in the advance travel, a secondMaltese-cross type drive means meshing with said reversely driven gearhaving a driving angle of a larger size as compared with the drivingangle of said first Maltese-cross type drive means for moving thecarriage in the return travel faster than in the advance travel, saidfirst and second Maltese-cross type drive means having pusher andbraking flanks and pusher and braking rolls corresponding to the pusherand braking flanks and associated toothed segments for drivingengagement with said reversely driven gear, said braking means of oneMaltese-cross type drive means being synchronized with the pusher meanson the second Maltese-cross type drive means for synchronizing theswivel angles of the reversely driven gear and said braking pusher meanson the second Maltese-cross type driving means being synchronized withthe pusher flank means on the first Maltese-cross type drive means forsynchronizing the swivel angles of the reversely driven gear.

8. In a mechanism for transmitting alternating forward and rearwardrotation to a reverse motion shaft; gear means fixedly mounted on saidshaft; a first Maltese-cross type gear means for driving said gear meansand having a driving angle for rotating said shaft in one directionrepresenting forward travel; a second Maltese-cross type drive means fordriving said gear means and having a driving angle of a larger size ascompared with the driving angle of said first Maltese-cross type drivemeans for rotating said shaft in a rearward direction representingrearward travel faster than in the forward travel; said secondMaltese-cross type drive means having speed change drive meansinterposed between the second Maltese-cross type drive means and thegear means fixed to the reverse motion shaft; said speed change drivemeans having synchronizing means portion causing synchronism of angle ofdrive with the first Maltese-cross drive means at the beginning of therearward drive motion of the reverse motion shaft, means portionaccelerating the rearward motion of the reverse motion shaft through agreater drive angle portion than the comparable acceleration drive forthe forward drive motion of the reverse motion shaft, means portiondriving said reverse motion shaft in the rearward direction at a fixedspeed greater than the comparable drive speed in the forward motion ofsaid shaft by the first Maltese-cross type drive means, means portionsdecelerating the rearward motion of the reverse motion shaft through agreater deceleration drive for the forward drive motion of the reversemotion shaft and synchronizing means causing synchronism of angle ofdrive with the first Maltese-cross drive means at the beginning of theforward drive motion of the reverse shaft.

9. In a mechanism for transmitting alternating forward and rearwardrotation to a reverse motion shaft, gear means fixedly mounted on saidshaft, a first constantly rotating shaft spaced from said reverse motionshaft, a first gear segment mounted on the first shaft, a pusher and abraking roll mounted respectively at the ends of said segment, andintermediate shaft mounted intermediate said reverse motion shaft andsaid first shaft, a first Maltese-cross like gear means having asegment, a pusher flank means and a braking flank means mounted on saidintermediate shaft for driving and braking engagement by said segmentand rolls on the first shaft, a reduction gear segment fixed to theintermediate shaft and meshing with said gear means on the reversemotion shaft, a second constantly rotating shaft rotating at the samespeed as the first shaft and in the same direction, a secondMaltese-cross type drive means including a gear segment on the secondshaft for meshing with said gear means on the reverse motion shaft, apusher roll and a braking roll at each end of said last named gearsegment and a pusher flank and a braking flank fixed to said reversemotion shaft and for cooperative driving action with said respectivelylast named pusher and braking rolls for driving the reverse motion shaftin a reverse direction of rotation and at a higher angular speed ofrotation than said first shaft, said reduction gear segment and saidmeans mounted on the intermediate shaft acting as speed change drivemeans and synchronizing means for synchronizing the speed of rotation ofsaid reverse motion shaft at the end of one direction of rotation withthe speed of rotation at the beginning of the reverse rotation of thereverse motion shaft and changing the speed of drive of the reversemotion shaft.

7 1.0. In a mechanism for transmitting alternating for- Ward andrearward rotation to a reverse motion shaft, gear means fixedly mountedon said shaft, a constantly rotating shaft, a first Maltese-cross typedrive means for driving said gear means and reverse motion shaft in onedirection, including pusher and braking flanks fixed to said reversemotion shaft, a gear segment fixed to said constantly rotating shaft formeshing and driving engagement with said gear means on the reversemotion shaft, a pusher roll and a braking roll at the ends of said gearsegment and for driving and braking action with said flanks,.anauxiliary shaft, an arcuate gear segment pivoted on said auxiliary shaftand meshing with said gear means to drive said reverse motion shaft at adifferent rate of rotation than said first Maltese-cross type drivemeans and in part of its arcuate travel causing a rotation in asynchronizing manner of the reverse motion shaft at one end of itsarcuate travel in one direction With the beginning of its arcuate travelin the reverse direction, said arcuate gear segment mounted on theauxiliary shaft having a balancer drive affixed thereto of a trueMaltesecross, said constantly rotating shaft having a pusher arm meansfixed thereto With a pusher thereon for driving engagement with saidbalaneer drive thereby driving said arcuate gear segment in onedirection when not being driven in. the reverse direction by said firstMaltese-cross type drive means.

11. In a mechanism for transmitting alternating for ward and rearwardrotation to a reverse motion shaft, said reverse motion shaft having ahigh speed gear segment and a low speed gear segment thereon, a firstconstantly rotating shaft, a second constantly rotating shaft} rotatingat the same speedbut in a reverse direction froth! said first constantlyrotating shaft, a Malte'se-cros'stype drive means drivingly disposedbetween the first constantly rotating shaft and the high speed gearsegment andineluding a gear segment, a pusher and a braking .flank andpusher and braking rolls for respective cooperation with said flanks, aMaltese-cross type drive means drivingly disposed between the secondconstantly rotatingshaft and the low speed gear segment on the reversemo tion shaft and including a gear segment, pusher and-1 braking flanksand pusher and braking rolls respectively for cooperation with the lastnamed flanks, said last I named flanks being shaped for cooperation withtheir re-;:

\ spective pusher and braking rolls to drive the reverse motion shaft ata rotation rate at the beginning: of its} low speed reverse motion thatis equal totherotation rate at the end of its just prior directionofrotation thereby synchronizing the deceleration speed of priordirection of i rotation with the acceleration speed at the beginning ofsaid reverse rotation.

References Cited in the file of this patent UNITED STATES PATENTS YeiderMay'S, 193=1-'

